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CTC
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Design Calculations
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C:\...\data\TutorialModel1.emvd
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Job Tag : Description :
Job Name : Drawing No :
CTC
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2015-02-19
Revision :
C:\...\data\TutorialModel1.emvd
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 2 prodia2 V33.2.2.4 Bentley Systems, Inc.
Table of Contents
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CTC
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Design Calculations
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Revision :
C:\...\data\TutorialModel1.emvd
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 3 prodia2 V33.2.2.4 Bentley Systems, Inc.
Codes, Guidelines and Standards Implemented.
Pressure vessel design code:
ASME VIII DIV.1 2013
Local load design method:
WRC 107 (1979-03)
Standard of flange ratings:
ASME B16.5-2009
Standard for pipes:
ASME B36.10M-2004/B36.19M-2004
Material standard(s) and update(s):
ASME II 2013 SA516GR60 Plate
ASME II 2013 SA106GRB Seamless pipe
ASME II 2013 SA105 Forging
Units:
SI
g = 9.80665 m/s2 [ Weight (N) = Mass (kg) × g ]
CTC
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C:\...\data\TutorialModel1.emvd
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 4 prodia2 V33.2.2.4 Bentley Systems, Inc.
Design Conditions.
Compartment 1 / /
Internal pressure : 1 MPa / /
Required MAWP : / /
Design Temperature : 200 °C / /
Height of liquid : 500 mm / /
Operating fluid spec. gravity : 1 / /
Corrosion : 3 mm / /
External pressure : -0.103 MPa / /
External temperature : 150 °C / /
Test Pressure : / /
Test fluid spec. gravity : 1 / /
Insulation Thickness : 100 mm / /
Weight/density of insulation : 35 kg/m3 / /
Radiography : Spot / /
Weld Type : Type 1 / /
CTC
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 5 prodia2 V33.2.2.4 Bentley Systems, Inc.
Allowable stresses and safety factors
ASME II part D
S Allowable tensile stress.
Sa allowable tensile stress under normal conditions.
ST Minimum value of tensile strength.
SY 0.2 Minimum value of yield strength 0.2 %.
SY 1.0 Minimum value of yield strength 1 %.
SRavg Average stress to cause rupture in 100,000 hours at design temperature.
Above room temperature, the value used is the lower of the room and at temperature values.
Compartment 1 Allowable tensile stress S
Materials Normal Conditions Exceptional and test
conditions Creep
Excluding
bolting
Carbon steel MIN{ (SY 0.2 / 1.5) , (ST / 3.5) } 0.9 × SY 0.2 SRavg / 1.5
Austenitic stainless
steel MIN{ (SY 1.0 / 1.5) , (ST / 3.5) } 0.9 × SY 1.0 SRavg / 1.5
Copper ? 0.9 × SY 0.2 SRavg / 1.5
Aluminium ? 0.9 × SY 0.2 SRavg / 1.5
Nickel ? 0.9 × SY 0.2 SRavg / 1.5
Titanium ? 0.9 × SY 0.2 SRavg / 1.5
Bolting
Carbon steel MIN{ (SY 0.2 / 4) , (ST / 5) } SY 0.2 / 2 SRavg / 1.5
Austenitic stainless
steel MIN{ (SY 1.0 / 4) , (ST / 5) } ST / 3 SRavg / 1.5
Cast materials 0.8 × S
Welded pipe 0.85 × S
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 6 prodia2 V33.2.2.4 Bentley Systems, Inc.
Hydraulic Test Pressure
ASME UG-99 (b) : Pt = 1.3 MAWP ( Sa / S )min
MAWP = maximum allowable pressure
P = Design Pressure
Sa = allowable stress at room temperature, normal operating conditions
S = allowable stress under normal operating conditions
For each component P
(MPa)
Sa
(MPa)
S
(MPa)
t
(mm)
c
(mm)
Pt
(MPa)
Elliptical Head (01) 30.10 1 118 118 10 3 1.3
Shell (02) 31.05 1 118 118 10 3 1.3
Shell (03) 31.05 1 118 118 10 3 1.3
Shell (04) 31.05 1 118 118 10 3 1.3
Elliptical Head (05) 30.11 1 118 118 10 3 1.3
Nozzle
M1
Neck
1
118 118 6.35 3 1.3
Pad 118 118 10 1.3
Flange 138 138 42.926 1.3
Bolting / / /
Nozzle
M2
Neck
1
118 118 6.35 3 1.3
Pad 118 118 10 1.3
Flange 138 138 42.926 1.3
Bolting / / /
Compartment 1 / /
MAWP 1 MPa / /
Test Pressure at the Top : 1.3 MPa / /
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For vertical vessels with a test in horizontal position : Pt’ = Pt + ∆Pt
∆Pt = additional hydrostatic pressure corresponding to the height of the vertical compartment.
Compartment 1 / /
Design Pressure P : 1 MPa / /
Test Pressure at the Top : 1.3 MPa / /
Hydrostatic pressure ∆Pt : / / /
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Hydrostatic Pressure
Type of
components
Operating Test
Specific
Gravity
Horizontal Vertical
Specific
Gravity
liquid level hydrostatic
height
Hydrostatic
pressure liquid level
hydrostatic
height
Hydrostatic
pressure liquid level
hydrostatic
height
Hydrostatic
pressure
(mm) (mm) (MPa) (mm) (mm) (MPa) (mm) (mm) (MPa)
Shell(s)
01 30.10 1 500.00 500.00 0.0049 1 1,380.00 1,380.00 0.0135 0.00 0.00 0.0000
02 31.05 1 500.00 500.00 0.0049 1 1,380.00 1,380.00 0.0135 0.00 0.00 0.0000
03 31.05 1 500.00 500.00 0.0049 1 1,380.00 1,380.00 0.0135 0.00 0.00 0.0000
04 31.05 1 500.00 500.00 0.0049 1 1,380.00 1,380.00 0.0135 0.00 0.00 0.0000
05 30.11 1 500.00 500.00 0.0049 1 1,380.00 1,380.00 0.0135 0.00 0.00 0.0000
Opening(s)
1 M1 1 / 0.00 0.0000 1 / 690.00 0.0068 / 0.00 0.0000
2 M2 1 / 0.00 0.0000 1 / 690.00 0.0068 / 0.00 0.0000
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Element(s) of geometry under internal pressure
Elliptical head (30.10) under internal pressure. ASME VIII DIV.1 2013 tn = nominal thickness E = Weld joint efficiency
So= Allowable stress T = Temperature
Sy = Yield Strength ET = modulus of elasticity
t = minimum required thickness Sa = allowable stress at room temperature
P = internal pressure ST = tensile strength at room temperature
D = inside diameter of straight flange σ = circular stress
R = inside radius of straight flange Pa = Max. allowable pressure
L = Inside radius Table UG-37 Ph = Hydrostatic pressure
r = Inside radius Table 1-4.4 Ca = corrosion + tolerance
Lsf = Straight flange = 50 mm Tol% = tolerance for pipes
tmin = (t+Ca)/Tol% shall be ≤ tn ts = (tn×Tol%)-Ca shall be ≥ t SA516GR60 Plate Schedule : / NPS : /
tn = 10.000 mm ST = 414 MPa Tol% = / PWHT : No Radiography : Spot
Seamless D/2h = 2 Cor. = 3 mm Tol. = 0 mm UG-16(b) = 1.5 mm
P (MPa) Ph (MPa) T (°C) So (MPa) Sy (MPa) ET (MPa) Sa (MPa)
Operation N
Horizontal test X
1.0049
1.3135
0.0049
0.0135
200
20
118
198.9
189
221
192,000
202,350
118
198.9
r (mm) L (mm) Do (mm) D (mm) R (mm) Ro (mm) h (mm)
Operation N
Horizontal test X
237.600
237.600
1,245.000
1,245.000
1,400.000
1,400.000
1,386.000
1,386.000
693.000
693.000
700.000
700.000
348.000
348.000
Appendix 1-4 (c)
K = 1/6 [2+(D/2h)2] t = PDK/(2SE-0.2P) σ = P [DK+ 0.2 ts] / (2E ts) Pa = 2S E ts / [DK+ 0.2 ts]
t = PDoK/[2SE+2P(K-0.1)] σ = P [DoK− 2ts(K-0.1)] / (2E ts) Pa = 2S E ts / [DoK− 2ts(K-0.1)]
S (MPa) E K ts (mm) σ (MPa) Pa (MPa) t (mm) tmin (mm)
Operation N
Horizontal test X
118
198.9
1
1
1
1
7.000
7.000
99.59
130.17
1.19
2.01
5.916
4.595
8.916
7.595
Appendix 1-4 (f) If 0.0005 ≤≤≤≤ ts/L < 0.002
r/D ≤ 0.08 : C1 = 9.31r/D−0.086
r/D > 0.08 : C1 = 0.692r/D+0.605
r/D ≤ 0.08 : C2 = 1.25
r/D > 0.08 : C2 = 1.46−2.6r/D
ϕ <β : c = a/[cos(β-ϕ)]
ϕ ≥β : c = a
a = 0.5D-r b = L−r Se = C1ET(ts/r) Re = c+r β = arc cos(a/b), rad ϕ = (Lts)0.5/r
Pe = ( )[ ]15.02
−rRRC
tS
ee
se Py = ( )[ ]15.02
−rRRC
tS
ee
sy
Pe/Py ≤ 1.0 : Pck = 0.6Pe
1.0 < Pe/Py ≤ 8.29 : Pck = 0.408Py +0.192Pe
Pe/Py > 8.29 : Pck = 2.0Py 5.1
ckP
shall be ≥ P
ts/L C1 C2 a (mm) b (mm) c (mm) Re (mm)
Operation N
Horizontal test X
0.0056
0.0056
/
/
/
/
/
/
/
/
/
/
/
/
Se (MPa) β (rad) ϕ (rad) Pe (MPa) Py (MPa) Pck (MPa) Pck /1.5 (MPa)
Operation N
Horizontal test X
/
/
/
/
/
/
/
/
/
/
/
/
/
/
Straight flange
UG-27 (c) t = PR/(SE-0.6P) σ = (PR / ts + 0.6P) / E Pa = S E ts / (R+ 0.6 ts)
Appendix 1-1 (a)(1) t = PRo/(SE+0.4P) σ = (PRo / ts − 0.4P) / E Pa = S E ts / (Ro− 0.4 ts)
S (MPa) E ts (mm) σ (MPa) Pa (MPa) t (mm) tmin (mm)
Operation N
Horizontal test X
118
198.9
1
1
7.000
7.000
100.09
130.83
1.18
2
5.941
4.611
8.941
7.611 MAWP (200 °C, Corroded) = 1.18 MPa MAWP (20 °C, new) = 1.7 MPa
Table UG-79-1 : Extreme fiber elongation ratio = 75 tn / Rf ( 1 - Rf / Ro ) = 3.13 % ( Rf = 239.6 mm ; Ro = +∞ )
t
Lsf D
h
R
CTC
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 10 prodia2 V33.2.2.4 Bentley Systems, Inc.
Cylindrical shell under internal pressure. ASME VIII DIV.1 2013
t = minimum required thickness tn = nominal thickness E = Weld joint efficiency
P = internal pressure S = Allowable stress T = Temperature
R = Internal Radius Ca = corrosion + tolerance σ = circular stress
Ro = outside radius Tol% = tolerance for pipes Pa = maximum allowable pressure
tn,min = (t+Ca)/Tol% shall be ≤ tn tu = (tn×Tol%)-Ca shall be ≥ t Ph = Hydrostatic pressure
UG-27 (c) t = P(R+Ca)/(SE-0.6P) σ = (P(R+Ca) / tu + 0.6P) / E Pa = S E tu / ((R+Ca)+ 0.6 tu)
Appendix 1-1.(a)(1) t = PRo/(SE+0.4P) σ = (PRo / tu − 0.4P) / E Pa = S E tu / (Ro− 0.4 tu)
Shell (02,03,04) : 31.05 (Barrel)
SA516GR60 Plate Schedule : / NPS : /
tn = 10.000 mm R = 690.00 mm Tol% = / PWHT : No Radiography : Spot
Ro = 700.00 mm Cor. = 3 mm Tol. = 0 mm UG-16(b) = 1.5 mm
P (MPa) Ph (MPa) T (°C) S (MPa) E tu (mm) σ (MPa) Pa (MPa) t (mm) tn,min
(mm)
Operation N
Horizontal test X
1.0049
1.3135
0.0049
0.0135
200
20
118
198.9
0.85
0.85
7.000
7.000
117.75
153.92
1.01
1.7
6.985
5.422
9.985
8.422
MAWP (200 °C, Corroded) = 1.01 MPa MAWP (20 °C, new) = 1.44 MPa
Table UG-79-1 : Extreme fiber elongation ratio = 50 tn / Rf ( 1 - Rf / Ro ) = 0.72 % ( Rf = 695 mm ; Ro = +∞ )
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 11 prodia2 V33.2.2.4 Bentley Systems, Inc.
Element(s) of geometry under external pressure External Pressure – Elliptical Head (Section No. 1) (in operation)
Elements considered :
Tag Diameter Thickness
modulus of
elasticity
Vacuum
curve Temperature
(mm) (mm) (MPa) (°C)
001 30.10 Head 1,400.00 10.000 199,900 CS-2 150.0 °C
ASME VIII DIV.1 2013 UG-33
External Pressure : P = 0.103 MPa modulus of elasticity : E = 199,900 MPa
Material : SA516GR60 Corrosion : 3 mm
Vacuum curve : CS-2 Tolerance : 0 mm
Thickness as new : tn = 10 mm External Diameter : Do = 1,400 mm
Checked thickness : t = 7 mm outside radius : Ro = /
outside height : ho = 355 mm Axis ratio : Do/(2ho) = 2
(d) Elliptical heads
Ko (Table UG-33.1) = 0.887 Equivalent outside radius Ro = Ko.Do = 1,242.25 mm
(a)(1)(a) : E = 1 ⇒ Pa(a) = 1.67 P = 0.713 MPa
UG-28 (d) : A =tRo
125.0= 0.000704 Pa(d) =
tR
B
o
= 0.4003 MPa
B (Subpart 3 Section II Part D or 0.0625E/(Ro/t)) = 71.047 MPa (a)(1)(b) Pa = MIN (Pa(a) , Pa(d)) = 0.4003 MPa ≥ P
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 12 prodia2 V33.2.2.4 Bentley Systems, Inc.
External Pressure – Stiffener No. 1 (in operation)
ASME VIII DIV.1 2013
Shell
External Pressure : P = 0.103 MPa Temperature : 150 °C
Material : SA516GR60 modulus of elasticity : E = 199,900 MPa
Vacuum curve : CS-2 Corrosion : 3 mm
Thickness as new : tn = 10 mm Tolerance : 0 mm
Checked thickness : t = 7 mm
Calculation length of previous section : L1 = 3,115 mm
Calculation length of next section : L2 = 3,115 mm
Stiffener
Type and dimensions : Plate 63.5 × 10 Material : SA516GR60
modulus of elasticity : E = 199,900 MPa Vacuum curve : CS-2
Cross-sectional area : As = 635 mm2 Diameter of shell at centroid elevation : Do = 1,400 mm
UG-29 Stiffened elements of cylindrical shells
ts1 = 7 mm 1o55.0
stD = 54.45 mm x1 = 45.36 mm
ts2 = 7 mm 2o55.0
stD = 54.45 mm x2 = 45.36 mm
B =ss
o
/4
3
LAt
DP
+= 544.4722 MPa Ls =
2
21 LL ++++= 3,115 mm teq = 7 mm
A (Subpart 3 Section II Part D FIG.G or 2B/E) = 0.000168 Is =
( )14
/ sss
2
o ALAtLD +=
606,082 mm4
Is ′ =( )
9.10
/ sss
2
o ALAtLD += /
I = 610,479.6 mm4 ≥ Is
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External Pressure - Summary (in operation)
Section No. 1 Component(s) Diameter (mm) Thickness (mm)
Length : 0 mm 1 [05] 1,400 10
ok (1)
Section No. 2 Component(s) Diameter (mm) Thickness (mm)
Length : 3,115 mm 1
2
3
[05]
[01]
[01]
1,400
1,400
1,400
10
10
10 ok (1)
Section No. 3 Component(s) Diameter (mm) Thickness (mm)
Length : 3,115 mm 3
4
5
[01]
[01]
[05]
1,400
1,400
1,400
10
10
10 ok (1)
Section No. 4 Component(s) Diameter (mm) Thickness (mm)
Length : 0 mm 5 [05] 1,400 10
ok (1)
(1) : # = unchecked element (revise design)
0 = unchecked element, without external pressure (P=0)
ok = checked element
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AutoPIPE Vessel (Microprotol) procal V33.2.2.4 14 prodia2 V33.2.2.4 Bentley Systems, Inc.
Vessel under combination loading Model for analysis of stress due to support.
Reactions per support, bending moment and shear loads are studied using a beam model on simple supported, with one of
the supports fixed either to the left or the right of the beam.
The beam is studied using the reduction process which is based on the Falk transmission matrices.
Support conditions allow for resolution of the moment and the rotation which are not subject to discontinuity when
crossing the support.
External single load and moment are applied at their acting point and are considered as a discontinuity similar to a change
in inertia or modulus of elasticity. Distributed loads do not constitute a discontinuity.
Reference axes are : beam x on the right, y up with positive loads down, moments > 0 from x to y.
Shell, liquid, and bundle own weight are considered as distributed loads while head weight, flange and cover, floating
head and nozzle are considered as concentrated loads.
Termination heads are removed and replaced as a concentrated load and an external moment. Hydrostatic height also
creates an external moment as a result of the hydrostatic pressure applied to its location
Each design case in analysed in the vertical and/or horizontal plane. The saddle reactions and bending moment used to
check shell stresses are the vector sum of the two planes. This also provides the new angle where the shell stress should
be checked
Thermal effects are considered by the friction factor to be an additional moment at the saddle location. A fixed saddle
balances all horizontal reactions. (µ = 0.3)
Principal stresses are f1 = 0.5[ ]σθ + σz + (σθ – σz)2 + 4 τ
2 and f2 = 0.5[ ]σθ + σz – (σθ – σz)
2 + 4 τ
2 and general primary
membrane stress intensity is σeq = , with σθ: circumferential stress , σz: longitudinal stress and τ: shear stress.
Saddle stresses are studied in the 3 axes.
For the purpose of wind and earthquake design, vibration periods are evaluated using the general modal equation
[k-ω².m] Φ = 0 and solving the eigenvectors and eigenvalues.
The flexibility matrix 1/k is derived using the beam analysis method, using successive unit loads applied at the mass
location.
The resulting dynamic matrix is 1/g.1/k.m where g = acceleration due to gravity and m = mass matrix.
Eigenvectors correspond to the natural modes and eigenvalues to their frequencies.
Subtracting the mode under study from the starting vector allows for study of the higher mode
The Dunkerley method is used for stacked vessels. This enables the global circular frequency to be determined to
1/ω2 = 2/ω1
2 where ω1 is the circular frequency of one vessel. The final period is T = 2π/ω
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Location of dominant stresses and worst cases.
Cases studied :
1 2
3
4
Operation Int.Max.P. (Corroded Weight) Lifting (New Weight)
Erected (New Weight)
During test Int.Max.P. (Corroded Weight)
5
6 7
Shutdown (Corroded Weight)
Operation Ext.P. (Corroded Weight) During test P = 0. (Corroded Weight)
(++) vertical downside and horizontal longitudinal to the right (−+) vertical upside and horizontal longitudinal to the right
(+−) vertical downside and horizontal longitudinal to the left (−−) vertical upside and horizontal longitudinal to the left
(+) vertical downside and horizontal cross (−) vertical upside and horizontal cross Verification of shell between the supports
1 02[01] Primary membrane stress intensity (highest point) 60.7 ≤ 118 MPa (51%)
6 03[01] Longitudinal compressive stress (highest point) 6.8 ≤ 90.9 MPa (8%) 1 03[01] Primary membrane stress intensity (lowest point) 61.1 ≤ 118 MPa (52%)
6 02[01] Longitudinal compressive stress (lowest point) 6.4 ≤ 90.9 MPa (7%)
6 03[01] Stability 0.7761 ≤ 1 (78%) Verification of shell in the plane of the supports
1 No. 2 Primary membrane stress intensity (highest point, left) 59.2 ≤ 118 MPa (50%) 1 No. 1 Primary membrane stress intensity (highest point, right) 59.2 ≤ 118 MPa (50%)
1 No. 2 Primary membrane stress intensity (lowest point, left) 55.2 ≤ 118 MPa (47%) 1 No. 1 Primary membrane stress intensity (lowest point, right) 55.2 ≤ 118 MPa (47%)
6 No. 1 Longitudinal compressive stress (highest point, left) 1.5 ≤ 90.9 MPa (2%)
6 No. 2 Longitudinal compressive stress (highest point, right) 1.5 ≤ 90.9 MPa (2%)
6 No. 2 Longitudinal compressive stress (lowest point, left) 10.1 ≤ 90.9 MPa (11%)
6 No. 1 Longitudinal compressive stress (lowest point, right) 10.1 ≤ 90.9 MPa (11%)
4 No. 2 Tangential shearing stress in the shell 10.4 ≤ 159.1 MPa (7%)
/ No. / Tangential shearing stress in the head /
/ No. / Circumferential stress (compression) (edge of support) /
4 No. 2 Circumferential stress (compression) (edge of the plate) 17.8 ≤ 198.9 MPa (9%)
4 No. 2 Circumferential stress (compression + bending) (edge of the support) 60.6 ≤ 248.6 MPa (24%)
/ No. / Circumferential stress (compression + bending) (edge of the plate) /
/ No. / Circumferential stress (compression + bending) (edge of the support + stiffener) /
/ No. / Circumferential stress (compression + bending) (edge of the plate + stiffener) /
/ No. / Circumferential stress (compression + bending) in stiffener (edge of the support) /
/ No. / Circumferential stress (compression + bending) in stiffener (edge of the plate) / Support check
4 No. 2 Stress at the low point of the saddle 6.4 ≤ 198.9 MPa (3%)
1 No. 2 Maximum bending stress 3 ≤ 170.1 MPa (2%)
4 No. 2 Compressive stress 2.3 ≤ 159.1 MPa (1%)
1 No. 2 Combined bending and compression 0.0287 ≤ 1 (3%)
2 No. 1 Tensile stress in the bolts -12.6 ≤ 100 MPa (-13%)
/ No. / Stability (Number of ribs ≤ 2) /
1 No. 1 Shear stress in the bolts 6.7 ≤ 100 MPa (7%)
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Case 1 - Operation Int.Max.P. (Corroded Weight) .
Moments and loads in plane of saddles.
N
o.
Support
saddles
Location (mm) Stiffness
(daN/mm)
Vertical Horizontal Combined
Reactions
(daN)
Shear
Loads (daN)
Bending
moments (daN·m)
Reactions Transverse (daN)
Shear
Loads (daN)
Bending
moments (daN·m)
Reactions Longitudinal
(daN)
Reactions
(daN)
Shear
Loads (daN)
Bending
moments (daN·m)
1 500.0 2,721.0 -852.1
1,869.0
-408.5
-1,012.8 0.0 0.0 0.0 864.7 2,721.0
-852.1
1,869.0
-408.5
-1,012.8
2 5,500.0 2,722.6 -1,869.4
853.1
-1,013.6
-409.3 0.0 0.0 0.0 -864.7 2,722.6
-1,869.4
853.1
-1,013.6
-409.3 Graph of bending moments and shear forces.
Vibration Periods and Center of Gravity.
Mode 1 2 3 4 5 Center of Gravity
Period 12.02659×10-3 s 3.337675×10-3 s 1.855573×10-3 s 1.324342×10-3 s 920.195×10-6 s 3,001 mm
maximum Longitudinal Bending Stress Verification.
Circumferential stress : σθ = (P+∆P± )R / t ∆P± : Hydrostatic pressure ft : allowable tensile stress
Longitudinal stress : σz = Pm R / 2t ± M K12 / π R2 t Pm : Pressure at the vessel equator fc : allowable compressive stress
General primary membrane stress intensity : σeq = MAX( | σθ - σz | ; | σz – 0.5 P |) K12 : Coef. EN 13445-3 (16.8-11)
Maximum allowable moment : Mmax = π R2 t fc Pmax : allowable external pressure
1,000 daN·m
Vertical
1 2
1,000 daN
1 2
1 daN·m
Horizontal
1 daN
Bending moments
Shear forces
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Component : 02[01] 31.05 P = 1 MPa
Maximum general primary membrane stress intensity : σeq shall be ≤ ft
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σθ (MPa) σz (MPa) σeq (MPa) El Ec ft (MPa)
500.0 - -1,014.7 696.5 1.3752 1.00 99.50 51.06 60.66 0.85 0.85 118.00 500.0 + -1,014.7 696.5 1.3752 1.00 99.50 48.44 60.07 0.85 0.85 118.00
Maximum longitudinal compressive stress : σz < 0 ⇒ |σz| shall be ≤ MIN( ft ; fc )
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σz (MPa) E ft (MPa) fc (MPa)
2,050.0 - 988.5 696.5 1.3752 1.00 48.48 1 118.00 82.17
500.0 + -1,014.7 696.5 1.3752 1.00 48.44 1 118.00 82.17
Proof of stability : |P| / Pmax + |M| / Mmax shall be ≤ 1.0 (P > 0 ⇒ P = 0)
Location = 500 mm fc = 82.17 MPa M = -1,014.7 daN·m Mmax = 87,662.7 daN·m Pmax = +∞ MPa Stab. = 0.0116 Component : 03[01] 31.05 P = 1 MPa
Maximum general primary membrane stress intensity : σeq shall be ≤ ft
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σθ (MPa) σz (MPa) σeq (MPa) El Ec ft (MPa)
3,000.0 - 1,328.9 696.5 1.3752 1.00 99.50 48.04 60.54 0.85 0.85 118.00
3,000.0 + 1,328.9 696.5 1.3752 1.00 99.50 51.46 61.13 0.85 0.85 118.00
Maximum longitudinal compressive stress : σz < 0 ⇒ |σz| shall be ≤ MIN( ft ; fc )
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σz (MPa) E ft (MPa) fc (MPa)
3,000.0 - 1,328.9 696.5 1.3752 1.00 48.04 1 118.00 82.17
4,050.0 + 912.9 696.5 1.3752 1.00 50.93 1 118.00 82.17
Proof of stability : |P| / Pmax + |M| / Mmax shall be ≤ 1.0 (P > 0 ⇒ P = 0)
Location = 3,000 mm fc = 82.17 MPa M = 1,328.9 daN·m Mmax = 87,662.7 daN·m Pmax = +∞ MPa Stab. = 0.0152 Component : 04[01] 31.05 P = 1 MPa
Maximum general primary membrane stress intensity : σeq shall be ≤ ft
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σθ (MPa) σz (MPa) σeq (MPa) El Ec ft (MPa)
5,499.0 - -1,013.6 696.5 1.3752 1.00 99.50 51.06 60.65 0.85 0.85 118.00 5,499.0 + -1,013.6 696.5 1.3752 1.00 99.50 48.44 60.07 0.85 0.85 118.00
Maximum longitudinal compressive stress : σz < 0 ⇒ |σz| shall be ≤ MIN( ft ; fc )
Location (mm) M (daN·m) R (mm) K12 Pm (MPa) σz (MPa) E ft (MPa) fc (MPa)
4,050.0 - 912.9 696.5 1.3752 1.00 48.57 1 118.00 82.17
5,499.0 + -1,013.6 696.5 1.3752 1.00 48.44 1 118.00 82.17
Proof of stability : |P| / Pmax + |M| / Mmax shall be ≤ 1.0 (P > 0 ⇒ P = 0)
Location = 5,499 mm fc = 82.17 MPa M = -1,013.6 daN·m Mmax = 87,662.7 daN·m Pmax = +∞ MPa Stab. = 0.0116
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Saddle No. 1
Calculation method : ASME + Zick information
Material of saddle : SA516GR60 Distance a = 500 mm
Pressure : P = 1 MPa Length L = 6,000 mm
Horizontal (longitudinal) reaction : RaHL = 864.7 daN Weight of saddle : Ws = 159.8 daN
Horizontal (cross) reaction : RaH = 0 daN Vertical Load : RaV = 2,721 daN
Maximum shear load : T = 1,869 daN Reaction at support : Q = 2,721 daN
Shell
Allowable stress S 118 MPa
Pad (not considered)
Allowable stress Sr /
All. compres. stress Sc 82.2 MPa Thickness tr 14 mm
Modulus of elasticity Ey 192,000 MPa Width b1 250 mm
Thickness t 7 mm Angle θ1 132.28 °
Mean radius Rm 696.5 mm θr = θ1 – 2.arctan (|RaH| / RaV) 132.28 °
Head
Allowable stress Sh 118 MPa b+1.56(Rm.t)0.5
= 358.9 mm
Thickness th 7 mm 2a = 1,250 mm θ +12° = 132 °
Depth h2 355 mm
Saddle
Yield Strength Leb 189 MPa
Stiffener
Allowable stress Ss / Width b 250 mm
Angle θ 120 °
θ = θ – 2.arctan (|RaH| / RaV) 120 °
Longitudinal stresses at the saddle level with a support
tRK
M
t2
R.P2
m1
1m*3
π−=σ = 53.34 MPa / 58.66 MPa
Si σ∗3 < 0 (Compressive) : | σ∗
3 | ≤ Sc
σeq = 53.84 MPa /59.16 MPa ≤ SE
tRK
M
t2
R.P2
m*1
1m*4
π+=σ = 47.76 MPa / 44.81 MPa
Si σ∗4 < 0 (Compressive) : | σ∗
4 | ≤ Sc
σeq = 52.23 MPa / 55.17 MPa ≤ SE
M1 = -408.54 daN·m / -1,012.83 daN·m ; K1 = 0.107 ; K*1 = 0.192 ; σeq = max ( |σθ − σ∗
3/4| , | σ∗3/4 + 0.5P| ) ;
σθ = P.Rm / t (P = 1.005 MPa) ; E = 1
shear stress
=2K 1.1707 τ2 = K2.T/(Rm.t) = 4.49 MPa ≤ 94.4 MPa
Circumferential stress
k = 1 x1 = 54.5 mm x2 = 54.5 mm
K5 (Table 4.15.1) = 0.7603 ( )( )ktxxbQK 2156 ++−=σ = -8.23 MPa 6σ ≤ S
K7 (Table 4.15.1) = 0.0305 ( ) 2
7
217
t2
QK3
xxbt4
Q−
++−
=σ = -28.1 MPa 7σ ≤ 1.25 S
Saddle check
Stress due to horizontal reaction on the saddle
K = (1+ cos β – 0.5 sin² β) / (π – β + sin β cos β) =0.2035 β = 2.0944 rad
H = K Q = 5,538 N Ab = 2,800 mm2 Sb = H / (2/3 Ab) = 2.97 MPa ≤ (90% Leb) (170.1 MPa)
Bending and compression stresses
Hb = 900 mm Mzz = RaH . Hb + RaH . (2Hb+ Ht) LEFF = 200 mm Mxx = RaHL . LEFF
Izz = 4.773029×109 mm
4 Szz = Izz/v = 9,358,883 mm
3 Ixx = 73.1371×10
6 mm
4 Sxx = Ixx/v = 585,096.8 mm
3
| Mzz | = 0 daN·m Sbz = | Mzz | / Szz | Mxx | = 172.95 daN·m Sbx = | Mxx | / Sxx
Sbz = 0 MPa ≤ (90% Leb) (170.1 MPa) Sbx = 2.96 MPa ≤ (90% Leb) (170.1 MPa)
A = 27,496 mm2 fb = 118 MPa Sbc = RaV / A Sbc = 0.99 MPa ≤ (0.8 fb ) (94.4 MPa)
max(Sbz ; Sbx ) / (90% Leb) + Sbc / (0.8 fb ) ≤ 1
Stability of web plate [CODAP C9.3.2.7] [AD S3/2 6.1.1]
hb2 = 550 mm lb = 1,212.4 mm eba = 14 mm Eb = 192,000 MPa fb = 90% Leb = 170.1 MPa
ε b = fb 103 / Eb x = hb2 / lb Kb = 1.255 ϕ = 0.522 Qmax = lb eba fb ϕ = 150,739.4 daN
Stresses in the bolts ( nb = 4 ; Sb = 324.3 mm2 ; xb = 580 mm )
Max. Tensile : σbT = max{ 0 ; [ |Mzz| / (xb. nb/2) – (RaV + WS) /nb ] / Sb } = -22.21 MPa ≤ 100 MPa
Max. Shear : σbL = [RaHL/ Sb] / nb = 6.67 MPa ≤ 100 MPa
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Saddle No. 2
Calculation method : ASME + Zick information
Material of saddle : SA516GR60 Distance a = 500 mm
Pressure : P = 1 MPa Length L = 6,000 mm
Horizontal (longitudinal) reaction : RaHL = -864.7 daN Weight of saddle : Ws = 159.8 daN
Horizontal (cross) reaction : RaH = 0 daN Vertical Load : RaV = 2,722.6 daN
Maximum shear load : T = 1,869.4 daN Reaction at support : Q = 2,722.6 daN
Shell
Allowable stress S 118 MPa
Pad (not considered)
Allowable stress Sr /
All. compres. stress Sc 82.2 MPa Thickness tr 14 mm
Modulus of elasticity Ey 192,000 MPa Width b1 250 mm
Thickness t 7 mm Angle θ1 132.28 °
Mean radius Rm 696.5 mm θr = θ1 – 2.arctan (|RaH| / RaV) 132.28 °
Head
Allowable stress Sh 118 MPa b+1.56(Rm.t)0.5
= 358.9 mm
Thickness th 7 mm 2a = 1,250 mm θ +12° = 132 °
Depth h2 355 mm
Saddle
Yield Strength Leb 189 MPa
Stiffener
Allowable stress Ss / Width b 250 mm
Angle θ 120 °
θ = θ – 2.arctan (|RaH| / RaV) 120 °
Longitudinal stresses at the saddle level with a support
tRK
M
t2
R.P2
m1
1m*3
π−=σ = 58.66 MPa / 53.35 MPa
Si σ∗3 < 0 (Compressive) : | σ∗
3 | ≤ Sc
σeq = 59.16 MPa /53.85 MPa ≤ SE
tRK
M
t2
R.P2
m*1
1m*4
π+=σ = 44.81 MPa / 47.76 MPa
Si σ∗4 < 0 (Compressive) : | σ∗
4 | ≤ Sc
σeq = 55.18 MPa / 52.23 MPa ≤ SE
M1 = -1,013.56 daN·m / -409.27 daN·m ; K1 = 0.107 ; K*1 = 0.192 ; σeq = max ( |σθ − σ∗
3/4| , | σ∗3/4 + 0.5P| ) ;
σθ = P.Rm / t (P = 1.005 MPa) ; E = 1
shear stress
=2K 1.1707 τ2 = K2.T/(Rm.t) = 4.49 MPa ≤ 94.4 MPa
Circumferential stress
k = 1 x1 = 54.5 mm x2 = 54.5 mm
K5 (Table 4.15.1) = 0.7603 ( )( )ktxxbQK 2156 ++−=σ = -8.24 MPa 6σ ≤ S
K7 (Table 4.15.1) = 0.0305 ( ) 2
7
217
t2
QK3
xxbt4
Q−
++−
=σ = -28.12 MPa 7σ ≤ 1.25 S
Saddle check
Stress due to horizontal reaction on the saddle
K = (1+ cos β – 0.5 sin² β) / (π – β + sin β cos β) =0.2035 β = 2.0944 rad
H = K Q = 5,541 N Ab = 2,800 mm2 Sb = H / (2/3 Ab) = 2.97 MPa ≤ (90% Leb) (170.1 MPa)
Bending and compression stresses
Hb = 900 mm Mzz = RaH . Hb + RaH . (2Hb+ Ht) LEFF = 200 mm Mxx = RaHL . LEFF
Izz = 3.422086×109 mm
4 Szz = Izz/v = 7,821,914 mm
3 Ixx = 73.10393×10
6 mm
4 Sxx = Ixx/v = 584,831.6 mm
3
| Mzz | = 0 daN·m Sbz = | Mzz | / Szz | Mxx | = 172.95 daN·m Sbx = | Mxx | / Sxx
Sbz = 0 MPa ≤ (90% Leb) (170.1 MPa) Sbx = 2.96 MPa ≤ (90% Leb) (170.1 MPa)
A = 25,466 mm2 fb = 118 MPa Sbc = RaV / A Sbc = 1.07 MPa ≤ (0.8 fb ) (94.4 MPa)
max(Sbz ; Sbx ) / (90% Leb) + Sbc / (0.8 fb ) ≤ 1
Stability of web plate [CODAP C9.3.2.7] [AD S3/2 6.1.1]
hb2 = 550 mm lb = 1,212.4 mm eba = 14 mm Eb = 192,000 MPa fb = 90% Leb = 170.1 MPa
ε b = fb 103 / Eb x = hb2 / lb Kb = 1.255 ϕ = 0.522 Qmax = lb eba fb ϕ = 150,739.4 daN
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Maximum Allowable Working Pressure Maximum Allowable Pressure(Geometry).
Type / Mark Diameter Thickness Max. allowable pressure Max. All. Ext. Pressure Hydrostatic pressure
Operating Test Operating Test Operating Test (mm) (mm) (MPa) (MPa) (MPa) (MPa) (MPa) (MPa)
01[05] 30.10 1,400.0 10.0 1.1847 1.9970 0.1351 / 0.0049 0.0135 /
02[01] 31.05 1,400.0 10.0 1.0070 1.6974 0.1351 / 0.0049 0.0135 /
03[01] 31.05 1,400.0 10.0 1.0070 1.6974 0.1037 / 0.0049 0.0135 /
04[01] 31.05 1,400.0 10.0 1.0070 1.6974 0.1351 / 0.0049 0.0135 /
05[05] 30.11 1,400.0 10.0 1.1847 1.9970 0.1351 / 0.0049 0.0135 /
Maximum Allowable Pressure (Nozzles).
Tag
Neck Flange Hydrostatic pressure
Operating Test Operating Test Operating Test
(MPa) (MPa) (MPa) (MPa) (MPa) (MPa)
M1 1.1923 2.1917 1.3800 3.0000 0.0000 0.0068 /
M2 1.1923 2.1917 1.3800 3.0000 0.0000 0.0068 /
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Maximum Allowable Pressure (compartment).
Compartment maximum pressure Max. External Pressure
Operating Test (shell)
Compartment 1 1.000 MPa (200 °C) 1.680 MPa 0.103 MPa (150 °C)
/ / / /
/ / / /
Without any additional pressure due to hydrostatic height.
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Isolated Opening(s) Figures for all configurations, from FIG. UG-37.1 And FIG UG-40.
Shell ( α = 0 ) or Cone ( α > 0 ) : in longitudinal plane.
Nozzle with or without pad, set-in or set-on Self-reinforcing nozzle, set-in or set-on
Cylindrical or conical shell: circumferential plane
Head: in the plane that contains the axis of the nozzle and the longitudinal axis of the vessel.
Nozzle with or without pad, set-in or set-on Self-reinforcing nozzle, set-in or set-on
β
h
d
R t
te
L2
tp L1
δ >90° δ < 90°
Pro
ject
ion
tn trn
tr
L<2.5tx L≥2.5tx te=0
tn
β
d
R t
Pro
ject
ion
tn
te 30°
tx
Sel
f
hei
gh
t
tx
γ
L1
β
tn
h R
t
te
L2
tp
α
Pro
ject
ion
d
trn
tr δ >90°
δ < 90°
β
tn
h R
t
te
α
Pro
ject
ion
d
30°
L≥2.5tx te=0
Sel
f
hei
gh
t
tn
tx
tx
L<2.5tx
γ
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Opening M1 [ in operation Int.P. ] Manhole ASME VIII DIV.1
Nozzle with pad (10×230) on Elliptical Head (No. 1) Set In
Pressure : P = 1 MPa Temperature : 200 °C
Shell Material :SA516GR60 Allowable stress : Sv = 118 MPa
Joint efficiency : 1 E1 = 1 Corrosion + tolerance : Cav = 3 mm Allowable stress : S = 118 MPa
Ext. Diameter : Do = 1,400 mm Thickness as new : 10 mm Tolerance for seamless pipe : /
Nozzle Neck Material : SA106GRB Allowable stress : Sn = 118 MPa
Weld joint efficiency : 1 Corrosion + tolerance : Can = 3 mm Tolerance for seamless pipe : 7/8
(12.5%)
Ext. Diameter : Don = 508 mm Thickness as new : 6.35 mm NPS 20"
External Projection : 435 mm Internal Projection : 0 mm Schedule: 10
Inclination : 0 ° Eccentricity : 0 mm
Flange Material : SA105 Type : WN
Rating : (ASME B16.5) 150 Height : 144.526 mm NPS 20"
Pad Material : SA516GR60 Allowable stress : Sp = 118 MPa
Height : 10 mm Pad : 230 mm Ext. Diameter : Dop = 968 mm
Weld Outside : leg41= 4 mm outer reinforcement : leg42= 5 mm Inside : leg43= /
fr1 =min(1,Sn/Sv) = 1 fr2 = min(1,Sn/Sv) = 1 fr3 = min(1,min(Sn, Sp)/Sv) = 1 fr4 = min(1,Sp/Sv) = 1 Required thickness of the nozzle neck Appendix 1-1
trn = P Ron / (SnE+0.4P) = 2.145 mm Ron = 254 mm E = 1
The nozzle neck thickness is adequate per Appendix 1-1.
Required thickness of the nozzle neck UG-45
ta = trn+Can= 5.15 mm ; tb1 = max[tUG-32 , UG-16(b)]+Cav= 0 mm ; tb3 = Table UG-45+Can= 0 mm
tUG-45 = max [ta , min [tb3 , tb1 ] ] = 5.145 mm
The nozzle neck thickness is adequate per UG-45.
Dimensions FIG. UG-40 angle of plane with longitudinal axis : Longitudinal plane : θ = 0° Circumferential plane : θ = 90°
angle of each side / wall of the vessel : δ = 90 ° δ = 90 ° δ = / δ = /
β = deflection angle / normal line 0 °
d = diameter of the opening 501.3 mm
Rn = radius of the finished opening 250.65 mm
ti = thickness of internal projection /
tp = Reinforcing ring width 230 mm
tx = thickness of selfreinforcing /
L = height of selfreinforcing / /
Configuration of the reinforcement : sketch (b-1) sketch (b-1)
te = thickness or height of the reinforcement 10 mm 10 mm
tn = Nozzle thickness 3.35 mm 3.35 mm
h = height of internal projection 0 mm 0 mm Reinforcement checking UG-37 opening M1 [ in operation Int.P. ]
Required thicknesses UG-37(a)
tr = 5.28 mm [ UG-37(a)(c) + UG-27(d) ] t = 7 mm K1 (Table UG-37) = 0.9 E = 1
trn = P Ron / (SnE+0.4P) = 2.145 mm Ron = 254 mm E = 1
Limits of reinforcement UG-40 : Longitudinal plane : θ = 0° Circumferential plane : θ = 90°
δ = 90 ° δ = 90 ° δ = / δ = /
UG-40 (b) : max [d , Rn+tn+t ] = 501.3 mm 501.3 mm
UG-40 (c) : min [ 2.5t , 2.5tn+te ] = 17.5 mm 17.5 mm Area required UG-37 (c) : Longitudinal plane : θ = 0° Circumferential plane : θ = 90°
F = Correction factor FIG.UG-37 1
A = d tr F + 2 tn/cos(β) tr F (1-fr1) 2,646.8 mm2
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Lengths and heights of calculation of the areas : Longitudinal plane : θ = 0° Circumferential plane : θ = 90°
δ = 90 ° δ = 90 ° δ = / δ = /
L1 = min [ UG-40(b)-Radius , length available ] 248.93 mm 248.93 mm
L2 = min [ UG-40(c) , height available ] 17.5 mm 17.5 mm
L3 = min [ h , 2.5t , 2.5ti ] = 0 mm 0 mm
L5 = min [ UG-40 (b)-Ron , tp , length available] 230 mm 230 mm
Area available (mm2) :
Longitudinal plane : θ = 0° Circumferential plane : θ = 90°
δ = 90 ° δ = 90 ° δ = / δ = /
A1 = L1 (E1 t-tr F) - tn/cos(β) (E1 t-tr F) (1-fr1) 428.2 428.2
A2 = L2 (tn-trn) fr2 21.1 21.1
A3 = L3 ti fr2 0 0
A41 = leg412 /2 fr3 8 8
A42 = leg422 /2 fr4 12.5 12.5
A43 = leg432 /2 fr2 0 0
A5 = L5 te fr4 2,300 2,300
A1 + A2 + A3 + A41 + A42 + A43 + A5 = 2,769.8 ≥A/2 2,769.8 ≥A/2
5,539.6 ≥A
The opening is adequately reinforced per UG-37.
Weld sizes check UW-16(c). opening M1 [ in operation Int.P. ]
Fig. UW-16.1 (d)+(a-1) full penetration weld
Minimum throat required actual
tc,inner min[¼ in.(6 mm);0.7×tmin]= 2.345 mm
tmin = min[ ¾ in.(19 mm) ; te , tn] 0.7×leg41 = 2.8 mm
tc,outer 0.5 × tmin = 3.5 mm
tmin = min[ ¾ in.(19 mm) ; te , t] 0.7×leg42 = 3.5 mm
tc min[¼ in. (6 mm);0.7×tmin]= /
tmin = min[ ¾ in.(19 mm) ; t , tn] 0.7×leg43 − Can = /
Weld sizes are adequate
Weld loads check UG-41(b). opening M1 [ in operation Int.P. ]
FIG. UG-41.1 (a) full penetration weld
Allowable Loads UW-15(c) + UG-41(a) + UG-45(c) + L-7
Outer fillet weld in shear :
sw,outer = π/4 × Dop × leg42 × 0.49 × min( Sp , Sv ) = 21,979.3 daN
Inner fillet weld in shear :
sw,inner = π/4 × Don × leg41 × 0.49 × min( Sp , Sn ) = 9,227.7 daN
Groove weld in shear :
sc = π/4 × Don × leg43 × 0.49 × min( Sn , Sv ) = 0 daN
Lower groove weld in tension :
sg,lower = π/4 × Don × t × 0.74 × min( Sn , Sv ) = 24,387.4 daN
Upper groove weld in tension :
sg,upper = π/4 × Don × te × 0.74 × min( Sn , Sp ) = 34,839.1 daN
Nozzle wall in shear :
sn = π/4 × (Don − tn) × tn × 0.70 × Sn = 10,967.4 daN
Loads to be carried by welds Fig. UG-41.1(a) Longitudinal plane : θ = 0° Circumferential plane : θ = 180°
δ = 90 ° δ = 90 ° δ = δ =
Total : W = [ A/2 − A1 + tn fr1 ( E1 t − F tr )] Sv 10,631.5 daN 10,631.5 daN
Path 1-1 : W1-1 = (A2+A5+A41+A42) Sv 27,630.7 daN 27,630.7 daN
Path 2-2 : W2-2 = (A2 +A3 +A41 +A43 +tn t fr1) Sv 619.9 daN 619.9 daN
Path 3-3 : W3-3 = (A2+A3+A5+A41+A42+A43+tn t fr1) Sv 27,907.4 daN 27,907.4 daN
Check weld strength paths Longitudinal plane : θ = 0° Circumferential plane : θ = 180°
δ = 90 ° δ = 90 ° δ = δ =
Path 1-1 : min(W;W1-1) ≤ sw,outer + s n Yes Yes
Path 2-2 : min(W;W2-2) ≤ sw,inner+sg,upper+sg,lower+sc Yes Yes
Path 3-3 : min( W , W3-3 ) ≤ sw,outer+sg,lower+sc Yes Yes
Strength of welded joints is adequate
t = 7
tc,inner
tc
leg41
leg43
te = 10
tc,outer
leg42
tn = 3.35
1 3
2
3 2
1
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Lifting accessories
Lifting a horizontal vessel with spreader
beam
Weight of vessel : WL = 3,269.2 daN
Weight considered WLC = 1.5 WL = 4,903.9 daN
Dist. Apart : L = 5,000 mm
LG = -0.8 mm
F1 = F2 = WL/2 = 2,451.9 daN
Lug verification. (1)
Allowable stress σa = 198.9 MPa
Yield Strength σe = 221 MPa
Lug L = 200 mm l = 12 mm
b = 115 mm h = 35 mm
D = 30 mm
Hole Location d1 = 70 mm d2 = 70 mm
Pad (Rectangular) LW = 200 mm lW = 100 mm
tW = 10 mm
Analysis thickness a = 0.7 min(l , tW ) = 7 mm
Reduction Factor α = min [0.8 (1+1/a), 1] = 0.914
Orientation α1 = 0 ° Sling load FC = 2,451.9 daN
Components Fx = FC sin(α1) = 0 daN
Fy = 0
Fz = FC cos(α1) = 2,451.9 daN
Shear stress Ssh = l min[b , h] = 420 mm2 σcis =(4/3) FC / Ssh = 77.84 MPa ≤ σa
Weld stress
Area A = (L + 2a) (l + 2a) – Ll = 3,164 mm2
Inertia Iy = 13,234,070 mm4 vmax = L / 2 = 100 mm
Bending stress : σflex = v Fx (d1 – tW) / Iy = 0 MPa shear : τ = Fx / A = 0 MPa
Normal stress : σ1 = Fz / A = 7.75 MPa
Total stress : =τ+σ+σ=σ 22
1 8.1)( flextot 7.75 MPa ≤ ασe = 202.06 MPa
Weld stress (Pad – Shell)
Area : AW = 4,396 mm2 Inertia IW = 26,436,600 mm
4
vW = (LW +2a) / 2 = 107 mm Normal stress : σ1W = Fz / AW = 5.58 MPa
Bending stress : σflexW = vW Fx d1 / IW= 0 MPa Shear : τW = Fx / AW = 0 MPa
Total stress : =τ+σ+σ=σ 2
W
2
WW1W 8.1)( flextot 5.58 MPa ≤ ασe = 202.06 MPa
F2 F1
WL
L
LG
l
Y
lW
h D
α1
b
L
d1
Z
X
LW
tW
d2
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Local loads on cylindrical shell (1) (Lifting Lug.), Loaded Area
WRC Bulletin 107 Design pressure code : ASME VIII DIV.1 2013
Design Pressure /
Existing circular stress /
Existing longitudinal stress /
Allowable Stress f = 118 MPa
Yield Strength 221 MPa
modulus of elasticity 202,350 MPa
Weld joint efficiency 0.85
Membrane stress factor 1.5
Design stress factor 3
Shell dimensions
Outside radius R = 700 mm
Thickness Ts = 10 mm
Corrosion allowance c = 0 mm
Reinforcing pad dimensions
Thickness (Tr) 10 mm
Data Loaded Area
Fillet radius 0 mm
1/2 Longitudinal length c2 = 100 mm
1/2 Circumferential length c1 = 6 mm
Geometric parameters
mean radius Rm = (R + Tr) - [(Tr + Ts -c)/2] =
700 mm γ = Rm / T = 35 Total thickness T = Tr + Ts - c = 20 mm
β1 = c1 / Rm = 0.0086 425.0 21 ≤ββ≤ ⇒ β1 = 0.0086
β2 = c2 / Rm = 0.1429 β2 = 0.0343 Factor β :
Radial load :
( ) 212
1 ββ1K11β
β
3
11β
−
−−= (si β1 / β2 > 1) ( ) 21
2
1 ββ2K1β
β1
3
41β
−
−−= (si β1 / β2 < 1)
Moment Mc : )3 212 ββKcβ = Moment ML : )3 2
21 ββKLβ =
Radial load P Bending Moment Mc Bending Moment ML
K1 K2 β Cc Kc β CL KL β Nφ 0.91 1.48 0.025 0.253 1.00 0.014 0.64 1.00 0.022
Nx 1.68 1.2 0.021 0.473 1.00 0.014 1.16 1.00 0.022
Mφ 1.76 0.88 0.015 / 1.27 0.017 / 0.879 0.019
Mx 1.2 1.25 0.021 / 1.714 0.023 / 1.212 0.026
Stress concentration factors
membrane Kn = 1
bending Kb = 1
Applied loads
Radial Load P = -3,467.561 daN Bending moment Mc = 0 daN·m
Shear Load Vc = 0 daN Bending moment ML = 0 daN·m
Shear Load VL = 0 daN Torsional moment Mt = 0 daN·m
DL
BL
Au
AL
Du
Bu
Cu CL
+
+
+
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Stresses Shell
(MPa) Points
Au AL Bu BL Cu CL Du DL
Longitudinal stresses (1) Kn (Nx / P / Rm) . P/ (RmT) -17.36 -17.36 -17.36 -17.36 -16.35 -16.35 -16.35 -16.35
(2) Kn (Nx / Mc / Rm2 β) . Mc / (Rm
2 β T) 0 0 0 0 0 0 0 0
(3) Kn (Nx / ML / Rm2 β) . ML / (Rm
2 β T) 0 0 0 0 0 0 0 0
(4) = (1) + (2) + (3) -17.36 -17.36 -17.36 -17.36 -16.35 -16.35 -16.35 -16.35
(5) Pressure 0 0 0 0 0 0 0 0
(6) σx,m = (4) + (5) -17.36 -17.36 -17.36 -17.36 -16.35 -16.35 -16.35 -16.35
(7) Kb (Mx / P) . 6 P/ T2 -104.03 104.03 -104.03 104.03 -78.02 78.02 -78.02 78.02
(8) Kb (Mx / Mc / Rm β) . 6 Mc / (Rm β T2) 0 0 0 0 0 0 0 0
(9) Kb (Mx / ML / Rm β) . 6 ML / (Rm β T2) 0 0 0 0 0 0 0 0
(10) = (7) + (8) + (9) -104.03 104.03 -104.03 104.03 -78.02 78.02 -78.02 78.02
Circumferential stresses (11) Kn (Nφ / P / Rm) . P/ Rm / T -16.35 -16.35 -16.35 -16.35 -17.1 -17.1 -17.1 -17.1
(12) Kn (Nφ / Mc / Rm2 β) . Mc / (Rm
2 β Τ) 0 0 0 0 0 0 0 0
(13) Kn (Nφ / ML / Rm2 β) . ML / (Rm
2 β Τ) 0 0 0 0 0 0 0 0
(14) = (11) + (12) + (13) -16.35 -16.35 -16.35 -16.35 -17.1 -17.1 -17.1 -17.1
(15) Pressure 0 0 0 0 0 0 0 0
(16) σφ,m = (14) + (15) -16.35 -16.35 -16.35 -16.35 -17.1 -17.1 -17.1 -17.1
(17) Kb (Mφ / P) . 6 P/ T2 -80.62 80.62 -80.62 80.62 -104.03 104.03 -104.03 104.03
(18) Kb (Mφ / Mc / Rm β) . 6 Mc / (Rm β Τ2) 0 0 0 0 0 0 0 0
(19) Kb (Mφ / ML / Rm β) . 6 ML / (Rm β Τ2) 0 0 0 0 0 0 0 0
(20) = (17) + (18) + (19) -80.62 80.62 -80.62 80.62 -104.03 104.03 -104.03 104.03
Shear stresses Circular Rectangular
(21) Vc / π ro T Vc / 4 c1 T 0 0 0 0 0 0 0 0
(22) VL / π ro T VL / 4 c2 T 0 0 0 0 0 0 0 0
(23) Mt / 2 π ro2 T 0 0 0 0 0 0 0 0 σx = (4) + (5) + (10) -121.39 86.67 -121.39 86.67 -94.37 61.67 -94.37 61.67
σφ = (14) + (15) + (20) -96.97 64.27 -96.97 64.27 -121.13 86.93 -121.13 86.93
τ = (21) + (22) + (23) 0 0 0 0 0 0 0 0
(24)
τ+σ−σ+σ+σ φφ
22
xx4)(5.0 -96.97 86.67 -96.97 86.67 -94.37 86.93 -94.37 86.93
(25)
τ+σ−σ−σ+σ φφ
22
xx4)(5.0 -121.39 64.27 -121.39 64.27 -121.13 61.67 -121.13 61.67
(26) = (24) – (25) = 22
x 4)( τ+σ−σφ 24.42 22.39 24.42 22.39 26.76 25.25 26.76 25.25
(27)
τ+σ−σ+σ+σ 22
mx,mφ,mx,mφ,4)(5.0 -16.35 -16.35 -16.35 -16.35 -16.35 -16.35 -16.35 -16.35
(28)
τ+σ−σ−σ+σ 22
mx,mφ,mx,mφ,4)(5.0 -17.36 -17.36 -17.36 -17.36 -17.1 -17.1 -17.1 -17.1
(29) = (27) – (28) = 22
mx,mφ, 4)( τ+σ−σ 1.01 1.01 1.01 1.01 0.75 0.75 0.75 0.75
actual Allowable
Total stress Max [ |(24)| , |(25)| , |(26)| ] = 121.39 MPa 354 MPa (3 f)
Membrane Stress Max [ |(27)| , |(28)| , |(29)| ] = 17.36 MPa 177 MPa (1.5 f)
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Read values Values used
Fig. 3C
Fig. 3C
γ = 50
γ = 15
( β = 0.021 )
( β = 0.021 )
9.9174
3.1328
(Pts A,B) Nx/(P/Rm) =
7.0097
Fig. 4C
Fig. 4C
γ = 50
γ = 35
( β = 0.021 )
( β = 0.021 )
9.6543
6.6
(Pts C,D) Nx/(P/Rm) =
6.6
Fig. 4C
Fig. 4C
γ = 50
γ = 35
( β = 0.025 )
( β = 0.025 )
9.6179
6.6
(Pts A,B) NΦ/(P/Rm) =
6.6
Fig. 3C
Fig. 3C
γ = 50
γ = 15
( β = 0.025 )
( β = 0.025 )
9.748
3.1132
(Pts C,D) NΦ/(P/Rm) =
6.9045
Fig. 2C-1
Fig. 2C-1
γ = 50
γ = 35
( β = 0.015 )
( β = 0.015 )
0.17
0.155
(Pts A,B) MΦ/P =
0.155
Fig. 1C
Fig. 1C
γ = 50
γ = 35
( β = 0.015 )
( β = 0.015 )
0.27
0.2
(Pts C,D) MΦ/P =
0.2
Fig. 1C-1
Fig. 1C-1
γ = 50
γ = 35
( β = 0.021 )
( β = 0.021 )
0.26
0.2
(Pts A,B) Mx/P =
0.2
Fig. 2C
Fig. 2C
γ = 50
γ = 35
( β = 0.021 )
( β = 0.021 )
0.2104
0.15
(Pts C,D) Mx/P =
0.15
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Minimum Design Metal Temperature ASME VIII DIV.1 2013
UCS-66
Curve Fig. UCS-66 ( A , B ,C , D ).
Er governing thickness UCS-66.
MDMTs (Fig. UCS-66 / Impact Test Temperature ) unadjusted MDMT
Ratio (Fig. UCS-66.1)
Re (Fig. UCS-66.1 / UCS-68(c)) temperature reduction
MDMTa adjusted MDMT
MDMT for each component.
Material Curve Er
(mm) MDMTs
(°C) Ratio
Re
(°C) MDMTa
(°C) 01 [05] 30.10 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
02 [01] 31.05 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
03 [01] 31.05 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
04 [01] 31.05 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
05 [05] 30.11 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
Nozzle M1 SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M2 SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Flange M1 SA105 B 5.56 -29 / n/a 0.725 15.4 / 0 -44.4
Flange M2 SA105 B 5.56 -29 / n/a 0.725 15.4 / 0 -44.4
Pad M1 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
Pad M2 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
MDMT for each assembly (joining base metal excluded).
Material Curve Er
(mm) MDMTs
(°C) Ratio
Re (°C)
MDMTa (°C)
01 [05] 30.10
02 [01] 31.05 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
01 [05] 30.10
Pad M1 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
02 [01] 31.05
03 [01] 31.05 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
03 [01] 31.05 04 [01] 31.05
SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
04 [01] 31.05
05 [05] 30.11 SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
05 [05] 30.11 Pad M2
SA516GR60 C 10 -45.5 / n/a 0.848 8.5 / 0 -48
Nozzle M1
01 [05] 30.10 SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M1 Pad M1
SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M1
Flange M1 SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M2 05 [05] 30.11
SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M2
Pad M2 SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Nozzle M2 Flange M2
SA106GRB B 5.56 -29 / n/a 0.839 9 / 0 -38
Rated MDMT of the vessel -38 °C ≤ Design MDMT -15 °C
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Circular stresses.
Type
Tag
Diameter
outside Length Thickness Operating Horizontal test Vertical test
(mm) (mm) (mm) (MPa) (MPa) (MPa)
01[05] 30.10 1,400.0 405.0 10.000 100.09 130.83 /
02[01] 31.05 1,400.0 2,000.0 10.000 117.75 153.92 /
03[01] 31.05 1,400.0 2,000.0 10.000 117.75 153.92 /
04[01] 31.05 1,400.0 1,900.0 10.000 117.75 153.92 /
05[05] 30.11 1,400.0 405.0 10.000 100.09 130.83 /
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Summary
[01]
[05]
[13]
Shell
Elliptical Head
Welding Neck Flange
Summary of nozzles [ Location and Dimensions ].
Tag
Location Dimensions (mm) Flange
Loc. Ori. Inc. Exc. Neck Reinforcement Projectio
n NPS Rating Typ.
(mm) (°) (°) (mm) Diam. Thk. Sch. NPS Type (a) (b)
M1 -100.0 0.00 0.00 0.00 508.00 6.350 10 20 Pad 10.000 230.00 435.00 20 150 [13]
M2 7,000.0 0.00 0.00 0.00 508.00 6.350 10 20 Pad 10.000 230.00 435.00 20 150 [13]
(a),(b) : Pad (ring) = thickness, Width ; Self Reinforcing = Height, over thickness ; Internal Plate = thickness, Height
NB : The external projection and the overthickness height of a self are measured along the axis of the nozzle.
Summary of nozzles [ Adjacent Openings, Goose and Material ].
Tag
Set
-in
(+
)
Set
-on
(-)
Op
erat
i
ng
Adjacent openings
Goose hydrostatic height Material
Radius Loc. Operating Test Neck Pad Flange
(mm) (mm) (mm) (mm)
M1 (+) H / / / 0.00 690.0 SA106GRB SA516GR60 SA105
M2 (+) H / / / 0.00 690.0 SA106GRB SA516GR60 SA105
Nozzle Type A = Process, H = manhole, E = With Blind Flange, L = Instrument, AP = Boot, XT = transition by head,
CA = Shell Inlet, CS = Shell Outlet, TA = Tubeside inlet, TS = Tubeside Outlet.
Summary of nozzles [ Type, Weight and Local Loads ].
Tag
Loc.
Op
erat
ing Mass Local Loads
Shell Nozzle Flange Longitudinal
Shear Load
Circumferential
Shear Load Radial Load
Longitudinal
Bending Moment
Circular Bending
Moment
Torsional
moment
No. (kg) (kg) (daN) (daN) (daN) (daN·m) (daN·m) (daN·m)
M1 01[05] H 67.5 215.0 0 0 0 0 0 0
M2 05[05] H 68.3 215.0 0 0 0 0 0 0
Nozzle Type A = Process, H = manhole, E = With Blind Flange, L = Instrument, AP = Boot, XT = transition by head,
CA = Shell Inlet, CS = Shell Outlet, TA = Tubeside inlet, TS = Tubeside Outlet.
Flange Weight With blind flange if present.
Summary of Stiffeners.
Stiffener Location
(mm)
Area
(mm2)
Inertia
(mm4)
Type and dimensions
(mm) Remarks
A 1 3,000.0 635.00 213,373 Plate 63.5 × 10
Stiffener: I = User Input M = Modified A = Added
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Summary of Forged Items. Flange dimensions
Tag Type
(1) (2)
External
Diameter
Internal
Diameter Bolt Circle
Flange
thickness Hub length
Cylindrical extension
length
Hub thickness
shellside
Hub thickness
flangeside
Nubbins
width
Stub
Thickness
(mm) (mm) (mm) (mm) (mm) (mm) (mm) (mm) (mm) (mm)
/ / / / / / / / / / / / /
(1) Flange Type : P = slip-on (loose), C = integral with hub, T = lap-type joint (loose),
R = slip-on (integral), G = Integral with hub, swing bolts
O = optional (corner joint), F = lap-joint on split ring, S = lap joint flange with removable segment(s) +
compression ring.
(2) Flange face: 0= flat face unconfined, 1= male-female semi-confined, 2= tongue and groove, 3= tongue and groove + nubbins.
Bolting
Tag (3) no.
[nB] Designation
Diameter Thread
length
Bolt Load
[FBO nom / nB]
Bolt torque
[Mt,nom]
Friction coefficient
in nut
[µ n]
Friction coefficient
in thread
[µ t]
Thread pitch
[ p t]
(mm) (mm) (N) (N·mm) (mm)
/ / / / / / / / / / / /
(3) Bolt Type : 1,2,4,6: ISO (1 and 4: Pitch 3 mm for Ø > M24) (1 and 6: Tensile Stress Area; 2,4: Root Area)
3: UNC, Root Area
5: ISO, Reduced Area (DIN 2510)
(4) Bolt torque in accordance
with EN 1591-1 Appendix D :
Mt,nom = kB × FBO nom / nB
kB = p t /(2π) + µ t × d t /(2cosα) + µ n × d n /2
d t = pitch diameter of the thread
d n = mean diameter in the nut (friction)
α = half angle of thread
(5) Bolt torque in accordance with EN 13445-3 Appendix G.8.4 :
(6) Bolt torque in accordance with GOST R 52857.4 Appendix J :
Gaskets
Tag Diameter
(mm)
Width
(mm)
Thickness
(mm)
Partition rib
width (mm)
Ring (mm)
Outer Width Internal Width Thickness
/ / / / / / / / Standard Flanges.
Type / Mark Norm Diameter
Nominal Rating
Material
Group
Temperature
(°C)
Pressure
(MPa)
Max. allowable
pressure (MPa)
[13] M1 ASME B16.5
ASME B16.5 NPS 20 150
SA105
1.1 1
200 °C 1 1.38
test 1.307 3
[13] M2 ASME B16.5
ASME B16.5 NPS 20 150
SA105
1.1 1
200 °C 1 1.38
test 1.307 3
Summary of Geometry.
Type
Tag
Diameter
outside Length
Cumulative
height Thickness Angle Mass Flanges
ratings
Specifi
c
Gravity Material
(mm) (mm) (mm) (mm) (°) (kg)
01[05] 30.10 1,400.0 405.0 50.0 10.000 0 176.5 7.85 SA516GR60
02[01] 31.05 1,400.0 2,000.0 2,050.0 10.000 0 685.6 7.85 SA516GR60
03[01] 31.05 1,400.0 2,000.0 4,050.0 10.000 0 685.6 7.85 SA516GR60
04[01] 31.05 1,400.0 1,900.0 5,950.0 10.000 0 651.3 7.85 SA516GR60
05[05] 30.11 1,400.0 405.0 5,950.0 10.000 0 176.5 7.85 SA516GR60
Angle : half angle at apex for a concentric cone ; maximum angle between cone and cylinder for an eccentric cone.
Material: (N) = normalized
NB: Italic line indicates an element for which the calculation under pressure has not been done.
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Summary of Weights, Capacities and Painting Areas.
Designation Mass (kg) Lifted Erected Operating Test Shutdown
Shells 2,022 X X X X X
Cones
Heads 353 X X X X X
Shell flanges
Skirts
Support saddles 326 X X X X X
Anchor boxes
Fireproofing
Man holes 566 X X X X X
Nozzles
Piping
Support Ring
Trays
Liquid on trays
Packing
Helicoidal plates
Internal lining
Insulation supports 43 X X X X X
Insulation (Vessel) 114 X X
Insulation (Piping)
Coil
Liquid in Coils
Stiffening rings 23 X X X X X
Piping Clips
Structural Clips
Ladders
Platforms
Tubesheets
Tubes and Tie Rods
Baffles and Support Baffles
Floating head flange
Split ring and splices
Internals
Operating
Test
Lifting
Erection
External loads
Operating
Test
Lifting
Erection
Compartment Compartment 1 / /
Capacity (m3) 9.662 / /
Mass (kg) Liquid
Operating 3,140 / /
Test 9,662 / /
Total Test 12,996 / /
Vessel
Mass (kg)
Operating 6,587
Lifted 3,334
Erected 3,334
Shutdown 6,587
Area (m2) Vessel Tag 32.3
Support 5.2 NB : New weight.
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Summary of saddles.
Standard : APVessel Number of saddles = 2 Fixed support No. = 1 Saddle No 1 (left)
Location = 500 mm Stiffness = / H = 900 mm Loose
Diameter =1,400 mm T = 120 ° Mass = 163 kg
4 Bolts : Diameter = 24 mm ( Hole Diameter = 30 mm ) Border Rib
Base Plate 2 Ribs Wear Plate Web
E
(mm)
B
(mm)
L
(mm)
C
(mm)
G
(mm)
EXV
(mm)
EYV
(mm)
K
(mm)
D
(mm)
M
(mm)
F
(mm)
FB
(mm)
EXF
(mm)
EXA
(mm)
a
(mm)
250 1,240 16 580 130 110 / 14 340 14 250 75 / 0 14 Saddle No 2 (right)
Location = 5,500 mm Stiffness = / H = 900 mm Loose
Diameter =1,400 mm T = 120 ° Mass = 163 kg
4 Bolts : Diameter = 24 mm ( Hole Diameter = 30 mm ) Border Rib
Base Plate 2 Ribs Wear Plate Web
E
(mm)
B
(mm)
L
(mm)
C
(mm)
G
(mm)
EXV
(mm)
EYV
(mm)
K
(mm)
D
(mm)
M
(mm)
F
(mm)
FB
(mm)
EXF
(mm)
EXA
(mm)
a
(mm)
250 1,095 16 580 130 110 / 14 340 14 250 75 / 0 14 Summary of Foundation Loads RaV : Vertical reaction in daN seismic load
RaHT : Horizontal (cross) reaction in daN (++) vertical downside and horizontal longitudinal to the right
RaHL : Horizontal (longitudinal) reaction in daN (+−) vertical downside and horizontal longitudinal to the left
AmT : Circumferential bending moment in daN·m (−+) vertical upside and horizontal longitudinal to the right
AmL : Longitudinal bending moment in daN·m (−−) vertical upside and horizontal longitudinal to the left
(+) vertical downside and horizontal cross
Stacked vessels: loads for the combined stack. (−) vertical upside and horizontal cross
Support No. 1 2 3 4 5 6 7 8 9 10
(Corr
oded
Wei
ght)
Op
erat
ion I
nt.
P.
Win
d
Norm
al
RaV 2,881 2,882
RaHT 0 0
RaHL 865 -865
AmT 0 0
AmL 0 0
(New
Wei
ght)
Lif
ting
RaV 1,634 1,635
RaHT 0 0
RaHL 0 0
AmT 0 0
AmL 0 0
a
EXA
F
E
EXA < 0
G
EXF
EXF
a
EXA
F
E
EXA > 0
G
EXF
EXF
a
G
F
E
EXA = 0
D
K
B
C L
H
M
FB
EXV
EYV
DB
EYV
T
CTC
My Address
My City
Design Calculations
2015-02-19
Revision :
C:\...\data\TutorialModel1.emvd
(2015-01-28)
AutoPIPE Vessel (Microprotol) procal V33.2.2.4 35 prodia2 V33.2.2.4 Bentley Systems, Inc.
(New
Wei
ght)
Ere
cted
RaV 1,634 1,635
RaHT 0 0
RaHL 0 0
AmT 0 0
AmL 0 0
(Corr
oded
Wei
ght)
Duri
ng t
est
RaV 6,024 6,026
RaHT 0 0
RaHL 0 0
AmT 0 0
AmL 0 0
(Corr
oded
Wei
ght)
Shutd
ow
n
Win
d
Norm
al
RaV 2,881 2,882
RaHT 0 0
RaHL 865 -865
AmT 0 0
AmL 0 0
(Corr
oded
Wei
ght)
Duri
ng t
est
P =
0.
RaV 6,024 6,026
RaHT 0 0
RaHL 0 0
AmT 0 0
AmL 0 0
CTC
My Address
My City
Design Calculations
2015-02-19
Revision :
C:\...\data\TutorialModel1.emvd
(2015-01-28)
AutoPIPE Vessel (Microprotol) procal V33.2.2.4 36 prodia2 V33.2.2.4 Bentley Systems, Inc.
List of customisable files. Materials C:\Users\Public\Documents\AutoPIPE Vessel\Config\Material.emdm (?)
Shapes
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimsha.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimsha.emsd (Tue Jul 22 18:21:28
2014)
Brackets /
Saddles
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimsad.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimsad.emsd (Tue Jul 22 18:21:26
2014)
Anchoring /
Gussets /
Legs /
Reinforcing pads
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpad.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpad.emsd (Tue Jul 22 18:21:26
2014)
Projection of nozzles
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpro.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpro.emsd (Tue Jul 22 18:21:26
2014)
Tubes
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpip.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\dimpip.emsd (Tue Jul 22 18:21:26
2014)
Pipe fittings /
Trade thickness /
Flanges
C:\Users\Public\Documents\AutoPIPE Vessel\Config\flangeAS.doc (Tue Jul 22 18:21:28
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\flangeAS.emsd (Tue Jul 22 18:21:28
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\StandardFlangeReferenceTable.doc
(Tue Jul 22 18:21:24 2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\StandardFlangeReferenceTable.emsd
(Tue Jul 22 18:21:24 2014)
Gaps for exchanger /
Bolts
C:\Users\Public\Documents\AutoPIPE Vessel\Config\boltUN.doc (Tue Jul 22 18:21:26
2014)
C:\Users\Public\Documents\AutoPIPE Vessel\Config\boltUN.emsd (Tue Jul 22 18:21:26
2014)
CTC
My Address
My City
Design Calculations
2015-02-19
Revision :
C:\...\data\TutorialModel1.emvd
(2015-01-28)
AutoPIPE Vessel (Microprotol) procal V33.2.2.4 37 prodia2 V33.2.2.4 Bentley Systems, Inc.
Summary of Errors and Warnings. No. Explanation ( the number is used for technical support )
Error (s) :
/
Warning (s) :
159 NOZZLES: no verification of multiple openings.
602 SADDLE n° 1 : the application conditions do not allow to the wear plate to be considered as a reinforcing plate.
602 SADDLE n° 2 : the application conditions do not allow to the wear plate to be considered as a reinforcing plate.
717 LIFTING : Lugs/trunnions are not placed at the same distance from the center of gravity.
Total: 0 error(s) and 4 warning(s).